JP2001208485A - Condenser - Google Patents

Abstract

PROBLEM TO BE SOLVED: To prevent a steam passage of a cooling unit from being blocked by water generated in the steam passage. SOLUTION: A condenser 4 comprises a cooling unit 12 for converting steam into water which has a plurality of steam passages 37 therein, a blower 64 for sucking water generated in the steam passages 37, and a recovering unit 33 for receiving the sucked water.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a condenser for converting a working medium in a gas phase into a liquid phase.

[0002]

2. Description of the Related Art Heretofore, as this type of condenser, there has been known a condenser having a cooling section in which a number of narrow passages for a cooling medium such as air and a number of narrow steam passages are alternately arranged.

[0003]

However, when the steam passage is narrow, the working medium in a liquid phase, for example, water, generated in the passage, blocks the passage due to factors such as surface tension. In such a case, there is a possibility that the flow rate of water vapor in the fuel cell is reduced, and condensing performance is reduced.

[0004]

SUMMARY OF THE INVENTION It is an object of the present invention to provide a condenser capable of preventing a working medium in a liquid phase generated in a passage of a cooling unit from blocking the passage. I do.

[0005] To achieve the above object, according to the present invention,
A cooling section having a plurality of working medium passages for converting the working medium in a gaseous state into a liquid state, and a suction for sucking the working medium in a liquid state generated in the working medium passages through the passages; Means and a condenser for receiving the sucked working medium in the liquid phase are provided.

With the above construction, the working medium in the liquid phase can be forcibly discharged from the inside of the passage, so that the flow rate of the working medium in the gas phase in the cooling unit is maintained and the original condensation performance is secured. can do.

[0007]

DESCRIPTION OF THE PREFERRED EMBODIMENTS A Rankine cycle system R shown in FIG. 1 uses an exhaust gas generated by an internal combustion engine 1 to raise the temperature of a high-pressure liquid, for example, water (a working medium in a liquid phase). Evaporator 2 that generates high-pressure steam (ie, a working medium in a gaseous state), that is, high-temperature high-pressure steam, and an expander 3 that generates an output by expanding the high-temperature high-pressure steam.
And a condenser 4, which is discharged from the expander 3 and has a reduced temperature and pressure due to the expansion, that is, a condenser 4 that liquefies the temperature-reduced pressure-reduced steam to produce water, and the water from the condenser 4 is supplied to the evaporator 2. And a supply pump 5 for supplying pressure.

In FIG. 2, the expander 3 has a substantially horizontal high-temperature and high-pressure steam inlet pipe 7 at the center of one end of a casing 6 thereof, and a plurality of temperature-reducing and pressure reducing pipes at the upper end of the other end of the casing 6. It has a steam outlet hole 8 and a substantially horizontal output shaft 9 at the center. The condenser 4 is attached to the expander 3 so as to receive the temperature-reduced pressure-reduced steam from each outlet 8.

The condenser 4 has a cylindrical housing 10.
The large diameter cylindrical portion 11 of the housing 10 has a cooling unit 12 for converting the temperature-reduced pressure-reduced steam into water. The cooling unit 12
It has a hollow cylindrical shape in which a plurality of annular panels 13 made of a metal material such as stainless steel, Al, etc. are overlapped, and has a steam introduction hole 15 formed by a hole 14 in each annular panel 13 at the center. The center line of the steam introduction hole 15 coincides with the axis of the output shaft 9.

An annular end plate 17 at one end of the steam guide tube 16 and a flange 18 at the outer periphery of the end plate 17 face the annular end surface of the cooling unit 12 on the expander 3 side. The unit is integrated with the cooling unit 12.
The hole 19 of the end plate 17 matches the steam introduction hole 15. The flange 20 at the other end of the steam guide tube 16 is a large-diameter tube portion 1.
One is overlapped with the flange 21 at one end, and is fixed to the flange 23 of the expander 3 by a plurality of bolts 22. As a result, each of the temperature-reduced and reduced-pressure steam outlet holes 8 of the expander 3 faces the inside of the steam guide tube 16.

The housing 10 has a divided small-diameter tube portion 24 disposed on the other end of the large-diameter tube portion 11, and a flange 25 of the small-diameter tube portion 24 faces the annular end surface of the cooling unit 12. , Its outer periphery is integrated with the cooling unit 12.

The output shaft 9 of the expander 3 is connected to the spline connection 2.
6, a transmission shaft 27 is mounted, and the transmission shaft 27 penetrates through the steam introduction hole 15 of the cooling unit 12 and the end wall 28 of the small-diameter cylindrical portion 24 to protrude to the outside, and has a bearing 29 on the end wall 28. It is rotatably supported through. In the end wall 28, two seal rings 31 for sealing between the shaft insertion hole 30 and the transmission shaft 27 existing outside the bearing 29 are formed.
7 is attached.

Referring also to FIGS. 3 and 4, a fixed guide tube 32 extending parallel to the transmission shaft 27 is provided in the lower portion of the housing 10.
And a collection pipe 33 slidably fitted in the guide pipe 32 and collecting water generated by cooling the temperature-reduced and reduced-pressure steam. The end of the recovery pipe 33 on the expander 3 side is closed, but the opposite end is open. Between the inner peripheral surface of the guide tube 32 and the outer peripheral surface of the collection tube 33, there is provided a collecting tube detent means comprising a key 34 and a key groove 35.

As shown in FIGS. 4 and 5, each annular panel 13 in the cooling section 12 has a group of ridges 36 formed by press working.
By brazing 6, a plurality of pipe-like steam passages (working medium passages) 37 are formed between the panels 13. The periphery of the hole 14 of both annular panels 13 is sealed by brazing of two arc-shaped ridges 38 whose upper parts are open, and communicates with the upper part of the steam introduction hole 15 between both ends of the arc-shaped ridges 38. An inlet 39 of the steam passage 37 is formed. The outer peripheral portions of both annular panels 13 are sealed over substantially the entire periphery by a combination of hemming and brazing, but are provided with cutouts located on the lower side and on the diameter that bisects the inlet 39. At 40, the hemming portion 41 is divided. The peripheral portion 42 of the notch 40 is fitted into one of a plurality of grooves 43 formed at a predetermined interval in the axial direction of the guide tube 32 and brazed. Thereby, the notch 4
0 coincides with the inner peripheral surface of the guide tube 32, and the outlet 44 of the steam passage 37 formed by the annular panels 13 is connected to the guide tube 3.
Face in 2.

At the end of the cooling unit 12 on the side of the expander 3, a steam passage 37 is formed by the cooperation of one annular panel 13, the annular end plate 17 and the flange 18, and the end on the side of the small-diameter cylinder 24. In the portion, a steam passage 37 is formed by cooperation of one annular panel 13, the flange 25 and the partition wall 45 on the inner peripheral side thereof. Each hemming part 41 is provided with a corresponding one of the grooves 4 of the comb-shaped spacing adjusting plate 46 extending in the generatrix direction of the cooling part 12.
7 (see also FIG. 12), and a plurality of the interval adjusting plates 46 are provided at predetermined intervals in the circumferential direction of the cooling unit 12.

As shown in FIG. 5, each steam passage 37 has one rising path 48 extending upward from the inlet 39 over the panel radius.
A plurality of branch paths 49 branching in the opposite and circumferential directions from the ascending path 48, a plurality of descending paths 50 connected to the lower side of each branch path 49, and a plurality of descending paths 50 connected to the lower side of each descending path 50. It comprises a plurality of focusing paths 51 and an outlet 44 at which the focusing paths 51 converge.

When the outlets 44 of the steam passages 37 are formed, as shown in FIG. 6, the converging paths 51 of the annular panels 13 whose entire outer peripheral portions are hemmed are formed in the grooves 43 of the guide tube 32.
And a portion of the hemming portion 41 and a portion in the vicinity thereof protrude into the guide tube 32.
Is brazed to the inner surface of the groove 43 of the guide tube 32. Thereafter, when the portion 52 of each of the annular panels 13 protruding into the guide tube 32 is cut off, the cutout portion 40 is formed, and the outlet 44 is opened there.

In this case, as shown in FIG. 8, the groove 43 has a wide portion 43a to be fitted to both annular panels B and a wide portion 4a.
3a has a narrow portion 43b which is open to the bottom surface and fits with the hemming portion 41, thereby securely sealing around the outlet 44 and increasing the bonding strength between each annular panel 13 and the guide tube 32. Can be.

As shown in FIGS. 4 and 9, a cooling air passage 54 as a cooling medium passage is formed between two adjacent steam passages 37, that is, forms each steam passage 54, and This is a gap between two facing annular panels 13. In order to secure the air passage 54, the annular panels 13 are provided with a plurality of small protrusions 55 that abut against each other. The inlet 56 of the air passage 54 is connected to the large-diameter cylindrical portion 1 of the housing 10.
The outlet 59 is located between the adjacent hemming portions 41 on the upper side of the annular panels 13 forming the vapor passage 37, while the outlet portion 59 is formed by the tube portion 58 existing in the lower bulging portion 57. Two annular panels 13 forming an air passage 54
In this case, the inner peripheral edge of the hole portion 14 is joined by a combination of hemming and brazing, and the sealing action of the hemming portion 60 allows the cooling air flow to enter the steam passage 37 and the steam air passage 54. To each other is prevented. The large-diameter cylindrical portion 11 has an outlet 5
9 is provided. Further, on the outer peripheral surface of the cooling unit 12, the space between the exhaust hood 61 and the lower bulging portion 57 is sealed by a pair of side panels 62.

When the outer peripheral portions of the two annular panels 13 forming the steam passage 37 are joined together by hemming and brazing as described above, the opening between the outer peripheral portions is prevented to reduce the air resistance, Thereby, the pressure loss of the condenser 4 can be reduced.

Since the condensation heat transfer coefficient of steam is much larger than the heat transfer coefficient of air convection, in order to make the cooling section 12 compact, the area of the cooling surface of the steam passage 37 is reduced. It is necessary to make the thermal resistance of both cooling surfaces equal by increasing the area of the cooling surface of the passage 54. Therefore, the ridge groups 36 of the adjacent panels 13 are joined to each other to form the steam passage 37 independently in a pipe shape, while the air passage 54 holds the adjacent panels 13 at a constant interval. The structure in which the two panels 13 facing each other do not contact each other is such that the area of the cooling surface of the air passage 54 is larger than that of the steam passage 37.

2 and 3, when the outlets 44 of the plurality of steam passages 37 are divided into a plurality of groups of the same number, the plurality of outlets 44 of each group 53 intermittently communicates with one of a plurality of circumferentially extending slot-shaped communication holes 63 formed at equal intervals along the axial direction.

As shown in FIGS.
A blower 64 is disposed in the small-diameter cylindrical portion 24 as suction means for forcibly sucking water generated in the steam passage 37 from the passage 37 through the outlet 44 and the communication hole 63.

The blower 64 includes a cylindrical casing 65 having a center line c at a position displaced by ε from the axis a of the transmission shaft 27, and a spline coupling portion 66 housed in the casing 65 and connected to the transmission shaft 27. And a plurality of vanes 69 slidably fitted in a plurality of radial grooves 68 of the rotor 67. The casing 65 includes a cylindrical main body 70 and the main body 70.
And a lid 71 which is detachable from the main body.
Is attached to the end wall portion 73 of the central cylindrical portion 72 in the partition wall 45 by a plurality of bolts 74.

A suction port 75 is provided at a lower portion of the casing 65, and the suction port 75 is integrated with the conduit 76 provided in the guide tube 32, the inner peripheral surface of the guide tube 32, and the large-diameter tube portion 53 in the recovery tube 33. The cylindrical space 78 between the outer peripheral surfaces of the small-diameter tube portion 77, the plurality of through holes 79 of the small-diameter tube portion 77, and the inside thereof communicate with the large-diameter tube portion 53 of the collection tube 33. On the other hand, a discharge port 80 is provided at an upper portion of the casing 65, and the discharge port 80 is provided through a through hole 82 formed in the small-diameter cylindrical portion 24 and the peripheral wall portion 81 in the central cylindrical portion 72 of the partition wall 45. It communicates with the steam introduction hole 15.

A hole 83 is formed below the end wall 28 of the small-diameter tube portion 24 to allow the small-diameter tube portion 77 to reciprocate. The end wall 28, the guide tube 32 and the like are formed so as to surround the hole 83. A water tank 84 as an element is provided. The inside of the small-diameter pipe portion 77 of the collection pipe 33 includes the through hole 79 and the cylindrical space 7.
Water tank 8 formed on the peripheral wall of guide tube 32 through
4 and an outlet 85 of the water tank 84.
b is connected to the suction port of the supply pump 5.

The large-diameter pipe portion 53 of the recovery pipe 33 is inserted into the guide pipe 32 so that the communication holes 63 in the large-diameter pipe section 53 of the recovery pipe 33 are sequentially communicated with the outlets 44 of the plurality of steam passages 37 of each group. A driving mechanism for reciprocating the motor is provided as follows.

That is, a boss 87 projecting from a center hole 86 of the lid 71 is provided at the center of the rotor 67 in the blower 64.
And a large-diameter gear 88 is attached to the boss portion 87 via a spline coupling portion 89. A gear holding cylinder 90 is rotatably fitted into the small diameter pipe portion 77 of the collection pipe 33, and a small diameter gear 93 is attached to the gear holding cylinder 90 via a spline coupling portion 92 between the pair of flange-like portions 91. The small-diameter gear 93 meshes with the large-diameter gear 88. The flange-like portions 91 are held between the end faces of the guide tube 32 and the end faces of the annular projecting portions 94 on the inner surface below the end wall 28. A cam groove 95 is formed on the outer peripheral surface of the small-diameter tube portion 77 as shown in FIG. 11 as a development, and a pin 96 engaging with the cam groove 95 is formed on the inner peripheral surface of the gear holding cylinder 90. It is held in an axial groove 97. Cam groove 9
The distance between the two chevron portions 98 of No. 5 is the stroke of the recovery pipe 33, which is within the range of this stroke, that is, one communication hole 63 communicates sequentially with the plurality of outlets 44 of one group.

In the above configuration, when the output shaft 9 rotates by the operation of the expander 3, the blower 64 operates via the transmission shaft 27 and the large-diameter gear 88 rotates. The rotation of the large-diameter gear 88 causes the small-diameter gear 93 to rotate.
The collecting pipe 33 reciprocates via the pin 96 and the cam groove 95, and the outlets 44 of the plurality of steam passages 37 of each group intermittently communicate with the inside of the collecting pipe 33 through the respective communication holes 63 of the collecting pipe 33. , A suction force acts on each outlet 44.

The temperature-reduced pressure-reduced steam discharged from each outlet hole 8 of the expander 3 passes through the steam guide tube 16 to the steam inlet hole 15 of the cooling unit 12, and from there to each steam passage 37 and its inlet 39. Enter from. The temperature-reduced pressure-reduced steam reaches a plurality of descending paths 50 via an ascending path 48 and a plurality of branch paths 49 of each steam path 37, and is cooled mainly by the cooling air flowing through the plurality of air paths 54 in the descending path 50. It becomes water. The water is forcibly sucked from the outlets 44 of the steam passages 37 by the suction force of the blower 64, and the communication holes 63.
And collects in the large-diameter tube portion 53 of the collection tube 33. Large diameter pipe 5
When the amount of water stored in 3 exceeds the predetermined amount, water is
7, the water tank 8 through the through hole 79 and the cylindrical space 78
4 from the inlet 85a.

As described above, when the water generated therefrom is forcibly discharged from each steam passage 37, it is possible to maintain the flow rate of the temperature-reduced and reduced-pressure steam in the cooling unit 12, thereby achieving the desired condensation performance. Can be secured.

When uncondensed vapor is generated, it is separated from water by the gas-liquid separation effect of the space in the large-diameter tube portion 53 of the recovery tube 33, and the small-diameter tube portion 77,
The suction port 7 passes through the through hole 79, the cylindrical space 78, and the conduit 76.
5 is sucked into the blower 64. And blower 64
From the outlet 80 to the steam inlet 15 of the cooling part 12 through the through-hole 82 in the small-diameter cylindrical portion 24 and the partition wall 45, and is returned to the steam passage 37 from there to be liquefied. . As a result, it is possible to avoid a decrease in water as a working medium in the Rankine cycle system R and to secure a necessary water amount.

In consideration of the thermal conductivity, surface treatment, weight reduction, recyclability, etc. of the cooling unit 12, each panel 13 is made of aluminum.
When it is composed of a system material (including pure Al and Al alloy), hydrogen, which is a non-condensable gas, is generated by a temperature-reduced pressure-reducing steam, that is, a chemical reaction between water vapor and the Al material, and most of the hydrogen is generated by water. Although discharged out of the steam passage 37, a part thereof stays in the narrow steam passage 37, and as a result, there is a possibility that the cooling effect on the temperature-reduced and reduced-pressure steam is hindered by the retained hydrogen. In this embodiment, when hydrogen is generated, the hydrogen can be circulated through the cooling unit 12, the recovery pipe 33, the blower 64, and the cooling unit 12 to prevent accumulation in the steam passage 37. it can.

Further, due to the forced discharge of water from the steam passage 37, even if the space between the adjacent panels 13 in the cooling unit 12 is made as small as possible, water accumulation can be avoided. Of the condenser 4 in the vehicle Rankine cycle system R can be improved.

Further, a plurality of steam passages 37 of each group
The outlet 44 and the communication holes 63 of the collection pipe 33 are intermittently connected, so that a large suction force can be applied to each outlet 63 even if a low-capacity blower 64 is used. Thereby, energy can be saved. This energy saving is particularly effective because the output of the expander 3 is used as the power source of the blower 64.

Furthermore, since the cylindrical cooling section 12 and the blower 64 are accommodated in the projection plane of the flange 23 of the expander 3, and the cooling section 12 is provided with the steam introduction hole 15 for temperature-reduced pressure reduction steam around its center line. , Inflator 3 and blower 64
It is possible to reduce the size of the assembly including the attached condenser 4.

FIG. 12 shows another example of the cooling unit 12. In this example, a laminated body composed of the panel 13 and the leaf spring 99 is set on a predetermined jig in a state where a spacing spring 99 is interposed between the adjacent panels 13 forming the air passage 54. The hemming portion 41 and the abutting double ridges 36 are brazed.

As a result, the hemming portions 41 and the ridges 36 are securely joined in a state where they are brought into contact with the elastic force of the leaf spring 99, thereby improving the strength and reliability.
Further, the interval between the air passages 54 can be maintained at a predetermined value.
In this case, prior to the hemming process, the two brazing materials installed in the processed portion are U-shaped portions u by the hemming process.
By sandwiching between the two opposing inner surfaces and the opposing surfaces of the flat plate portion p located therebetween, the soldering work of each hemming portion 41 can be facilitated and the joining strength can be increased. This is the same for each hemming unit 60.

In this example, two types of annular panels 13 having different arrangement positions of the ridge groups 36 are used so that the branch passages 49 of the adjacent steam passages 37 are arranged in a zigzag manner. . The overall structure of the cooling unit 12 using such an annular panel 13 is as shown in FIG.

[0040]

According to the present invention, the above configuration prevents the working medium in the liquid phase generated in the passage of the cooling unit from blocking the passage, thereby securing the desired condensation performance. Capable of providing a condenser.

[Brief description of the drawings]

FIG. 1 is an explanatory diagram of a Rankine cycle system.

FIG. 2 is a vertical sectional front view of the condenser.

FIG. 3 is an enlarged view of a main part of FIG. 2;

FIG. 4 is an explanatory diagram illustrating an example of a structure of a cooling unit and a collecting unit.

5 is a sectional view taken along line 5-5 of FIG. 2 and corresponds to a sectional view taken along line 5-5 of FIG. 4;

FIG. 6 is a cross-sectional view showing a state where a part of an annular panel is fitted in a groove of a guide tube.

FIG. 7 is a cross-sectional view showing a state where a portion of the annular panel protruding into the guide tube is cut away.

8 is a view taken in the direction of arrow 8 in FIG. 7;

9 is a sectional view taken along line 9-9 of FIG. 2 and corresponds to a sectional view taken along line 9-9 of FIG. 4;

FIG. 10 is a sectional view taken along line 10-10 of FIG. 2;

FIG. 11 is a development view of a cam groove.

FIG. 12 is a sectional view of a main part of another example of the cooling unit.

FIG. 13 is an explanatory diagram showing another example of the structure of the cooling unit and the collecting unit.

[Explanation of symbols]

 12 Cooling part 33 Recovery pipe (Recovery part) 37 Steam passage 39 Inlet 44 Outlet 64 Blower (suction means)

 ──────────────────────────────────────────────────続 き Continuing on the front page (72) Inventor Tsutomu Takahashi 1-4-1, Chuo, Wako, Saitama Prefecture Inside Honda R & D Co., Ltd. (72) Taizo Kitamura 1-4-1, Chuo, Wako, Saitama Prefecture Inside Honda R & D Co., Ltd. (72) Inventor ▲ Takashi Takashi 1-4-1 Chuo, Wako-shi, Saitama F-term inside Honda R & D Co., Ltd. 3G081 BA20 BD03 DA07

Claims (2)

[Claims] 1. A cooling section (12) having a plurality of working medium passages (37) and a cooling medium formed in the working medium passages (37) for converting a working medium in a gaseous state into a liquid state. A condenser comprising suction means (64) for sucking the liquid-phase working medium from the passage, and a collecting part (33) for receiving the sucked liquid-phase working medium. 2. A suction side of the suction means (64) communicates with an outlet (44) side of the working medium passage (37), and a discharge side thereof has an inlet (3) of the working medium passage (37).
The condenser according to claim 1, which communicates with the side (9).